EP2724861A2 - Presse à feuilles et procédé de fonctionnement d'une presse à feuilles - Google Patents

Presse à feuilles et procédé de fonctionnement d'une presse à feuilles Download PDF

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Publication number
EP2724861A2
EP2724861A2 EP13189614.4A EP13189614A EP2724861A2 EP 2724861 A2 EP2724861 A2 EP 2724861A2 EP 13189614 A EP13189614 A EP 13189614A EP 2724861 A2 EP2724861 A2 EP 2724861A2
Authority
EP
European Patent Office
Prior art keywords
drive
cylinder
printing
torsional vibration
printing machine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP13189614.4A
Other languages
German (de)
English (en)
Other versions
EP2724861B1 (fr
EP2724861A3 (fr
Inventor
Nicolai Kubasiak
Thomas Herrmann
Dr.-Ing. Holger Wiese
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Manroland Sheetfed GmbH
Original Assignee
Manroland Sheetfed GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Manroland Sheetfed GmbH filed Critical Manroland Sheetfed GmbH
Publication of EP2724861A2 publication Critical patent/EP2724861A2/fr
Publication of EP2724861A3 publication Critical patent/EP2724861A3/fr
Application granted granted Critical
Publication of EP2724861B1 publication Critical patent/EP2724861B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/004—Electric or hydraulic features of drives
    • B41F13/0045—Electric driving devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/008—Mechanical features of drives, e.g. gears, clutches
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/08—Cylinders
    • B41F13/20—Supports for bearings or supports for forme, offset, or impression cylinders
    • B41F13/21—Bearer rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/002—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion characterised by the control method or circuitry
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D19/00—Control of mechanical oscillations, e.g. of amplitude, of frequency, of phase
    • G05D19/02—Control of mechanical oscillations, e.g. of amplitude, of frequency, of phase characterised by the use of electric means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41P—INDEXING SCHEME RELATING TO PRINTING, LINING MACHINES, TYPEWRITERS, AND TO STAMPS
    • B41P2213/00—Arrangements for actuating or driving printing presses; Auxiliary devices or processes
    • B41P2213/70—Driving devices associated with particular installations or situations
    • B41P2213/73—Driving devices for multicolour presses
    • B41P2213/734—Driving devices for multicolour presses each printing unit being driven by its own electric motor, i.e. electric shaft

Definitions

  • the invention relates to a printing machine, in particular a sheet-fed printing machine, according to the preamble of claim 1. Furthermore, the invention relates to a method for operating a printing press, in particular a sheet-fed press, according to the preamble of claim.
  • a printing machine such. As a sheet-fed press, a substrate is moved through several printing units of the printing press to print on the substrate.
  • Each printing unit of a printing machine has a form cylinder, a rolling on the forme cylinder transfer cylinder, a rolling on the transfer cylinder impression cylinder and an inking unit and preferably a dampening unit.
  • At least one printing plate is arranged on the forme cylinder, whereby forme cylinders are also referred to as plate cylinders.
  • At least one transfer mold is arranged on the transfer cylinder, wherein transfer cylinders are also referred to as rubber cylinders.
  • the present invention relates to a printing press with multiple printing units and with multiple drives.
  • the drives thereby drive into printing units, namely into a cylinder of the printing units.
  • Each drive of the printing press is assigned a separate drive controller, the drive together with the respective drive forms a drive control loop.
  • the respective drive controller generates an actuating signal for the corresponding drive of the drive control loop on the basis of a deviation between a nominal value and an actual value.
  • the cylinders of the printing units can form the printing quality negatively influencing torsional vibrations.
  • Such torsional vibrations arise in a printing machine, for example, by internal influences due to non-uniform movements of different mechanisms such as the gripper controls, the Vorgreiferantrieb, the wet and / or Farbwalzenanlauf on the channel edge, and the repercussions of the Verreibungsantriebes or by the so-called lift.
  • vibrational excitations from the printing press known.
  • the vibrations do not form synchronously with the respective suggestions, especially since the vibration excitations usually occur offset in a distributed over the entire machine unevenly distributed timing. Rather, the vibrations are formed in accordance with the respective stiffness, mass inertia and damping in the various drive ranges.
  • the detection of the occurring torsional vibrations is required.
  • An oscillation state is detected via incremental rotary encoders on the blanket cylinder or transfer cylinder or blanket cylinder.
  • the measurement is first carried out as a rotation angle signal, from which then after a single derivation possibly also a vibration angular velocity can be determined.
  • the analysis of state variables corresponding to the course of the process serves on the one hand for the control-technical synchronization of rubber or transfer or blanket cylinders and form or plate cylinders. On the other hand, but should also be the signal recording of torsional vibrations. The comparison of the measured values with a setpoint then provides information about the vibration parameters. An additional perception of the torsional vibrations can also take place via the measurable electrical current which is fed to the direct drive motor of the plate or forme cylinder.
  • a sheet-fed printing machine is provided in each printing unit with a forme cylinder, a rolling on the forme cylinder, a rolling on the blanket cylinder impression cylinder, an inking unit with inking rollers and a dampening unit with a rolling on the forme dampening form roller.
  • the dampening rollers are driven under conditions of continuous pressure in a delta operation with a surface speed deviating from the form cylinder.
  • the form cylinder of each printing unit is assigned to the intrinsic motor drive a direct drive.
  • the blanket cylinder, the impression cylinder, the inking unit and the dampening unit are driven by a main drive of the sheet-fed press.
  • a control or control device controls the direct drive in the continuous printing operation so that it runs synchronously to the main drive.
  • the direct drive of the respective forme cylinder is controlled so that when the dampening roller of the dampening unit rolls over a tensioning channel on the forme cylinder, the direct drive continues to run synchronously with the main drive, despite the synchronization deviation caused thereby.
  • This control is carried out at an angle and thus synchronously to the channel pass on a respective form cylinder
  • further control signals for the main drive and / or the direct drives of the forme cylinders of the printing press are to be generated from the synchronism control deviations of all printing units involved in the printing in order to realize a vibration compensation for the printing press.
  • the synchronous control deviations of the printing units should be compared with the vibration behavior of the printing press, with a higher-level control device therefrom generating control signals for the main drive of the printing press and / or the direct drives of the forme cylinder.
  • the disadvantage here is that the targeted influencing of certain disturbances on the forme cylinder drive is not sufficient only with regard to its concrete emergence event in order to influence the overall vibration behavior effectively.
  • the assignment of a higher-level control system for switching actuating signals for torsional vibration compensation on all drives ignores the fact that a printing press as a complex oscillatory structure produces different vibration states in different machine areas which are not uniformly combated.
  • a printing press and a method for operating a printing press In a known sheet-fed printing machine several printing units and multiple drives are provided.
  • the drives drive in printing units each via a cylinder.
  • Each drive is assigned a separate drive controller which generates a control signal for the corresponding drive based on a deviation between a setpoint and an actual value.
  • a specific torsional vibration compensation quantity is generated, which is valid only in a specific drive control loop for torsional vibration compensation. So it can only be ensured that in a multi-color printing machine with one or more main drive motors and with separate drives for each individual plate or forme cylinder of each printing unit, the vibrations at the location of the drives can be influenced.
  • a vibration damping measure provided for the oscillating overall system (drive train).
  • the present invention is based on the problem to provide a novel printing press and a novel method for operating a printing press.
  • the drive controllers of the direct drives of the forme cylinders are each assigned at least one device which generates an independent variable for the compensation of torsional vibrations during operation of the printing machine from at least one state variable of the drive control loops into which the respective drive controllers are integrated of the main drives and / or the printing unit parts connected to the main drive (s).
  • the respectively determined torsional vibration compensation variable according to the invention is valid exclusively for torsional vibration compensation by means of a direct drive of a forme cylinder in the respectively affected drive control loop.
  • At least one state variable of each of the drive control loops for the direct drives of the printing machine for the drive controller of this drive control loop generates a torsional vibration compensation variable which is valid or used exclusively in this drive control loop for torsional vibration compensation. No modal analysis of the press is required for this.
  • the rotational vibration compensation variable generated for the respective drive controller with the aid of the device can be the current regulation, speed regulation and / or position control of the respective drive controller are used.
  • the torsional vibration compensation variable can be a current variable, rotational speed variable or position variable which is acted upon as compensation variable of the current control, rotational speed control or position control. So here is preferably the control of the synchronous operation between rubber or blanket or transfer cylinder and form or plate cylinder and an additional compensation of noise from machine vibrations at least the main drive by parallel to the control mode of the self-drive generated compensation sizes allows the compensation variables as power -, speed or position size can be pronounced.
  • each device associated with a drive controller comprises means for detecting a rotational vibration of the driven cylinder to be compensated from state variables of the respective drive control loop, and for generating the torsional vibration compensation variable from the detected torsional vibration.
  • the means of the device associated with the drive controller in this case comprise a function whose parameters are adaptable in the sense of an adaptation during operation of the printing press.
  • a counter-phase admission of a self-propelled drive or individual drive motor can take place with a correspondingly dimensioned control current.
  • the control effect on the oscillating overall system is exercised separately and as required by each drive controller or self-propelled cylinder of a forme cylinder.
  • the hereby implicitly present modal vibration components can be compensated, without having to know the proper movements of the main drive in its entirety. Elaborate methods for identifying the vibrations to be compensated by modal analysis are therefore not required. As a result, a modal coordination of the individual actuators to influence the vibration among themselves is also not required.
  • the regulator arrangement not only serves a sole, locally limited compensation of possible plate cylinder torsional vibrations.
  • the control effect in the sense of an active torsional vibration compensation extends beyond the immediate drive range of the plate or plate cylinder, in particular to the lower part of the printing machine, ie the gear train in the main drive of the printing machine. It is essential here that a vibration damping is to take place via a mechanical coupling by means of rolling contacts in the area of the bearer rings between the blanket or transfer cylinder and the forming or plate cylinder of each printing unit and other rolling contacts, even though there is no gear connection between the cylinders the plate or plate cylinder yes by means of self-propelled independently of the mechanically coupled cylinders.
  • the transmission of a controlled damping effect on vibrations is possible in principle, because a rolling contact between the bearer rings in the range of the desired operating states of the machine has a sufficiently large radial and tangential stiffness.
  • the existing in the rolling of the bearer rings of rubber and plate cylinder radial and tangential coupling act like stiff springs in a dynamic overall system.
  • the tangential coupling is also carried out within certain settlement differences arising from diameter tolerances between the bearer rings of rubber and plate cylinder and occur as Dehnschlupf in the stiction state of Hertzian contact.
  • each printing unit of a sheet-fed offset printing press already has a potential feed point for compensating torques. This can largely be ruled out that there are non-compensable natural vibration modes, because the feed points are at the location of a vibration node or close to a vibration node. So if a random feed point in a node to happen should come to rest, but the other feed-in points with high security are not in a node and can take over the compensation function.
  • the rotary encoder system associated with the respective drive motor implicitly supplies the information about modal oscillation components present in this area of the drive system, and these can also be compensated by the associated motor.
  • a spectrally differentiated compensation with harmonic counter moments nor a modal coordination of the individual actuators is necessary.
  • the inventive method is characterized by a high level of robustness and reliability and by the use of multiple drive motors also by a high efficiency with minimized additional effort for the active torsional vibration compensation.
  • FIG. 1 to 2 for a sheet-fed press comprising four printing units 10, 11, 12 and 13.
  • Each of the printing units 10 to 13 of the sheet-fed printing press comprises according to Fig. 1 an impression cylinder 14, a transfer cylinder 15, an inking unit 16 and a forme cylinder 17.
  • each printing unit may also include a dampening unit.
  • Form cylinder 15, inking unit 16 and transfer cylinder 17 are in FIG. 1 to represent the functional context symbolically represented as small circles. The actual size ratios are in FIG. 2 shown.
  • a transfer cylinder 18 is positioned in order to transfer to printing substrate B between the individual printing units 10 to 13.
  • the sheet-fed printing machine has one or more main drives 19 and 19 ', wherein the main drive or drives 19, 19' drive directly or indirectly via a transmission element into one of the impression cylinders 14 of the printing unit 10.
  • the closed gear train RZ is symbolically indicated here as a dashed connecting line between the cylinder centers and couples all transporting cylinder or drums 14, 18 executed elements of the sheet printing machine and the transfer cylinder 15 torsionally rigid and in fixed rotational relationship with each other.
  • Each form cylinder 17 is associated with a separate direct drive 20 to drive the form cylinder 17 of all printing units 10 to 13 own motor.
  • Each form cylinder 17 of each printing unit 10 to 13 can be uncoupled via a clutch 21 from the closed gear train RZ, in which all impression cylinders 14, transfer cylinder 15 and transfer cylinder 18 are integrated be.
  • a coupling 28 may be provided in the drive train between the gear train RZ and the inking unit 16, so that the inking units 16 can be driven or disconnected via the gear train RZ ( Fig. 2 ). In normal printing operation while the inking units 16 are connected by means of the clutches 28 with the gear train RZ.
  • the drives of the inking units 16 can be separated from the gear train RZ by means of the clutches 28. Switching through the drives, so that all clutches 21, 28 are closed, takes place only in safety-relevant emergency situations or when setting up the printing press.
  • a rotation angle correlation between the rotating elements in the region of the gear train RZ which is fixedly determined by gears
  • a rotation angle correlation between the forme cylinders 17 and the transfer cylinders 15 in the respective printing units 10 to 13 is also provided.
  • FIG. 1 is the connection between the two cylinders 17 and 15 designated as a rolling contact RK symbolic.
  • a mechanical synchronization support is made possible. This mechanical synchronization is performed on the basis of later-described races (bearer rings 26, 27) attached to respective cylinders 15, 17.
  • Fig. 2 shows details of the drive condition and the drive controls of the form cylinder 17 of the printing units 10 to 13 by the same respective associated direct drives 20th
  • each form cylinder 17 of the printing units 10 to 13 is associated with a cooperating with the forme cylinder 17 transfer cylinder 15.
  • These first work together in the area of their work surfaces to transfer a color image.
  • the forme cylinder 17 each front side of the work surface limiting and rigidly connected to the cylinder body bearer rings 26 assigned as races.
  • the transfer cylinder 15 each end face the work surface limiting and rigidly connected to the cylinder body bearing rings 27 assigned as races.
  • the unwinding is carried out so that the rolling contact allows relative movements for a so-called printing length correction between the forme cylinder 17 and the transfer cylinder 15.
  • a controlled advance or lag the forme cylinder 17 relative to the transfer cylinder 15 performs. This process of advancing or retarding is cyclically repeated at each revolution of the cylinder so that the corrective action for each printing operation can be performed in the same manner.
  • the rolling contact of the bearer rings 26, 27 under pressure is described at each point by a radial stiffness C R and a tangential stiffness C T between the bearer rings due to Hertzian pressure.
  • a mechanical coupling is given by the contact of the bearer rings 26, 27 between the transfer cylinder 15 and the forme cylinder 17 of each printing unit 10 to 13 and the other rolling contacts.
  • Said mechanical coupling is basically given when the Hertzian contact between the bearer rings 26, 27 has a sufficiently high radial rigidity C R and also tangential stiffness C T.
  • a resulting radial and tangential coupling acts as a stiff spring in a dynamic overall system.
  • the tangential coupling is due to Dehnschlupf in the stiction state of Hertzian contact also within certain settlement differences such as diameter tolerances and targeted differential movements between the bearer rings 26, 27 as in a process step of the above-described printing length correction between transfer cylinder 15 and forme cylinder 17th
  • each direct drive 20 of each printing unit 10, 11, 12 and 13 is assigned a respective drive controller 22.
  • the controller 22 generates based on a control deviation between a setpoint and an actual value a manipulated variable for the direct drive 20 of the printing unit.
  • the actual value is preferably a position actual value of the forme cylinder 17 to be driven by the direct drive 20 of the respective printing unit, this position actual value of the forme cylinder 17 being provided by a position encoder 23 associated therewith.
  • the desired value is preferably the position actual value of the transfer cylinder 15 of the respective printing group 10, 11, 12 or 13 cooperating with the forme cylinder 17, this position actual value of the transfer cylinder 15 being provided by a position sensor 24 assigned to it.
  • a control deviation between this actual value and this setpoint is, as already mentioned, supplied to the drive controller 22, wherein the drive controller 22 generates an actuating signal for the direct drive 20 of the forme cylinder 17 of the respective printing unit 10, 11, 12 or 13 based on this control deviation.
  • Fig. 3 a frontal view of the printing unit after Fig. 2 shown.
  • Form cylinder 17, transfer cylinder 15 and impression cylinder 14 are rotatably mounted respectively on journal Z in a left and a right frame wall 29.
  • the forme cylinder 17 carries a printing plate for producing a color image by means of a Farbrrelles of the inking unit 16th
  • the transfer cylinder 15 carries a blanket or blanket, by means of which the color image in the rolling gap between the forme cylinder 17 and transfer cylinder 15 is removed from the printing plate.
  • the counter-pressure cylinder 14 finally carries as a sheet leading cylinder a system of grippers, not shown, for guiding of printing material during the printing process.
  • Left and right end of the form cylinder 17 and the transfer cylinder 15 are each the bearer rings 26, 27 mounted rotatably connected to the respective cylinder body.
  • the bearer rings 26 arranged on the forme cylinder 17 in each case roll on a corresponding bearer ring 27, which is arranged on the transfer cylinder 15.
  • the impression cylinder 14 and the transfer cylinder 15 are drivingly coupled by gears of the gear train RZ torsionally rigid with each other.
  • the gear train RZ is in turn assigned to the main drive 19.
  • the form cylinder 17, however, the direct drive 20 is assigned.
  • the rotary encoder 23 is rotatably coupled to the rotational position measurement.
  • one of the bearing pin Z of the transfer cylinder 15 is rotationally fixed coupled to the rotary position measurement of the encoder 24.
  • each drive controller 22 is assigned to each direct drive 20 of each printing unit 10 to 13 such a device 25 and 31 which generates a valid only for the respective drive controller 22 torsional vibration compensation quantity.
  • the illustrated embodiment serves as a state variable for the device 25, from which the torsional vibration compensation quantity is generated online during operation, the actual value of the respective drive control loop, namely the actual position of the corresponding forme cylinder 17, so the measurement signal of the encoder 23. Also, as a state variable from the the torsional vibration compensation quantity is generated online during operation, a motor current or a motor rotational speed of the direct drive 20 or any other control state variable of the respective drive control loop are used.
  • the state variable for the device 31, from which the torsional vibration compensation variable is generated online during operation is the actual value of the respective drive control loop, namely the actual position of the corresponding transfer cylinder 15, ie the measuring signal of the rotary encoder 24.
  • the device 31 and device 25 associated with each drive controller 22 of each direct drive 20 each have a first means for converting from the or each state variable of the respective drive control loop, here the actual position value of the transfer cylinder 15 or the forme cylinder 17, a torsional vibration of the driven one of the transfer cylinder to be compensated 15 or form cylinder 17 to detect. Furthermore, this device 31 and device 25 has a second means for generating from the detected torsional vibration the torsional vibration compensation variable for the respective drive control loop. This torsional vibration compensation quantity is added to the control signal Synchronization of the rotational movements of form cylinder 17 and transfer cylinder 15 superimposed.
  • the control arrangement with the drive controllers 22 is used according to the invention now not only a sole, localized compensation possible torsional vibrations of the forme cylinder 17.
  • the control effect in the sense of an active torsional vibration compensation extends beyond the immediate area of each forme cylinder 17 on the transfer cylinder 15 and thus on the lower part the printing machine (gear train RZ) via the mechanical coupling of the bearer ring contacts between the respective transfer cylinders 15 and cylinders 17 of each of the printing units 10 to 13.
  • the regulation according to the invention for torsional vibration compensation changes online during the operation of the printing machine in the sense of an adaptation.
  • the first means and the second means of a device 31 and / or device 25 assigned to each drive controller 22 each comprise at least one function, wherein at least one parameter of these functions in the sense of an adaptation can be adapted online during the operation of the printing press.
  • the adaptation can be based on the evaluation of an additional criterion, such. As a maximum lag error or temporary lag error, to particularly interesting operating points, in order to generate correspondingly adapted torsional vibration compensation variables.
  • the torsional vibration compensation quantities are time-variable compensation quantities.
  • each printing unit 10 to 13 each associated with a direct drive 20, independent of the other printing units online during the operation of the printing press a torsional vibration compensation.
  • This torsional vibration compensation is done using the already existing rotary encoder 23, 24 of the forme cylinder 17 and transfer cylinder 15 of the respective printing units 10 to 13.
  • each drive controller 22 of each direct drive 20 of each printing unit is assigned a device 31 and / or device 25 for torsional vibration compensation, which individually generates a torsional vibration compensation variable for each drive controller 22 and thus for each printing unit 10 to 13.
  • FIGS. 1 and 3 illustrated arrangement of a drive system for a printing unit with in a first subsystem via a gear train RZ coupled drive range, which is driven by a central main drive 19, and a separately driven by a direct drive 20 second subsystem of the drive mechanical coupling via a rolling contact between the two subsystems is usable for influencing the vibration behavior of the entire drive system.
  • the coupling of a moment for vibration damping takes place starting from one or more direct drives 20 with respect to the longitudinal axes of the printing cylinder virtually symmetrical on the rolling contacts of the bearer rings 26, 27 of form cylinder 17 and blanket cylinder 15.
  • the encoder system associated with a respective drive motor which may have, for example, optical incremental encoders, provides the oscillation information about compensatable modal oscillation components present in this area of the drive system, and precisely these can be provided by the associated drive motor also be compensated.
  • the method according to the invention is characterized by a high level of robustness and reliability as well as by the use of several motors also by a high efficiency with minimized additional expenditure for the active torsional vibration compensation.
  • the devices 31 and 25 can be used simultaneously or alternatively, so that torsional vibration compensation based on the movement of the forme cylinder 17 and / or the transfer cylinder 15 can take place.
  • a controlled torsional vibration compensation is performed so that on the one hand as a result of each given vibration state in the range of the gear train RZ compensation is possible and that on the other hand, the torsional vibration compensation is performed adapted to each locally present vibration state in the range of one of the printing units 10 to 13.
  • an active vibration damping for example, by the fact that the higher-frequency speed or bearing vibrations in the drive control loop is not followed 100%, just to counteract these vibrations so can.
  • This measure can be done, for example, by an additional compensation variable superimposed on the position control.
  • limit torque must not be exceeded, which are specified by the drive system.
  • the limit torques refer to the transmittable torques in the friction drives between the cylinders, which on the one hand affect the synchronization and on the other hand ensure the transmission of the damping moments.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Engineering & Computer Science (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Inking, Control Or Cleaning Of Printing Machines (AREA)
  • Rotary Presses (AREA)
EP13189614.4A 2012-10-23 2013-10-22 Presse à feuilles et procédé de fonctionnement d'une presse à feuilles Active EP2724861B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012219334 2012-10-23
DE102013110459.2A DE102013110459A1 (de) 2012-10-23 2013-09-23 Druckmaschine und Verfahren zum Betreiben einer Druckmaschine

Publications (3)

Publication Number Publication Date
EP2724861A2 true EP2724861A2 (fr) 2014-04-30
EP2724861A3 EP2724861A3 (fr) 2017-09-27
EP2724861B1 EP2724861B1 (fr) 2021-04-28

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EP (1) EP2724861B1 (fr)
DE (1) DE102013110459A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015217990B4 (de) * 2014-09-18 2021-04-22 Koenig & Bauer Ag Bogenoffsetdruckmaschine

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1202147B1 (fr) 2000-10-26 2004-12-22 Heidelberger Druckmaschinen Aktiengesellschaft Procédé pour compenser des vibrations mécaniques dans des machines
DE102005041697A1 (de) 2005-09-02 2007-03-15 Man Roland Druckmaschinen Ag Druckmaschine
DE102007020727A1 (de) 2007-05-03 2008-11-13 Manroland Ag Druckmaschine und Verfahren zum Betreiben einer Druckmaschine

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19545114A1 (de) * 1995-12-04 1997-06-05 Heidelberger Druckmasch Ag Antrieb für mehrere Übertragungszylinder einer Druckmaschine
DE19623224C1 (de) * 1996-06-11 1997-09-11 Roland Man Druckmasch Antrieb für eine Druckmaschine
DE102008009203B4 (de) * 2007-03-02 2019-04-25 Heidelberger Druckmaschinen Ag Druckmaschine mit verstellbaren Schmitzringen und Verfahren zum aktiven Gegeneinanderverdrehen von Zylinderpaaren
DE102009045737B4 (de) * 2009-10-15 2012-10-04 manroland sheetfed GmbH Verfahren zum Betreiben einer Druckmaschine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1202147B1 (fr) 2000-10-26 2004-12-22 Heidelberger Druckmaschinen Aktiengesellschaft Procédé pour compenser des vibrations mécaniques dans des machines
DE102005041697A1 (de) 2005-09-02 2007-03-15 Man Roland Druckmaschinen Ag Druckmaschine
DE102007020727A1 (de) 2007-05-03 2008-11-13 Manroland Ag Druckmaschine und Verfahren zum Betreiben einer Druckmaschine

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DE102013110459A1 (de) 2014-04-24
EP2724861B1 (fr) 2021-04-28
EP2724861A3 (fr) 2017-09-27

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